WO2007006493A1 - Systeme de garniture d'etancheite a bagues coulissantes - Google Patents

Systeme de garniture d'etancheite a bagues coulissantes Download PDF

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Publication number
WO2007006493A1
WO2007006493A1 PCT/EP2006/006635 EP2006006635W WO2007006493A1 WO 2007006493 A1 WO2007006493 A1 WO 2007006493A1 EP 2006006635 W EP2006006635 W EP 2006006635W WO 2007006493 A1 WO2007006493 A1 WO 2007006493A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
mechanical seal
seal ring
slide ring
sealing
Prior art date
Application number
PCT/EP2006/006635
Other languages
German (de)
English (en)
Inventor
Andreas Schrüfer
Manfred Oppler
Günther Lederer
Armin Laxander
Klaus Lang
Rolf Johannes
Andreas Fesl
Peter Dröscher
Original Assignee
Burgmann Industries Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Burgmann Industries Gmbh & Co. Kg filed Critical Burgmann Industries Gmbh & Co. Kg
Priority to EA200800323A priority Critical patent/EA012134B1/ru
Priority to JP2008520762A priority patent/JP4848008B2/ja
Priority to US11/922,129 priority patent/US8523186B2/en
Priority to AT06776137T priority patent/ATE455265T1/de
Priority to DE502006005919T priority patent/DE502006005919D1/de
Priority to EP06776137A priority patent/EP1902239B1/fr
Publication of WO2007006493A1 publication Critical patent/WO2007006493A1/fr
Priority to NO20076214A priority patent/NO338115B1/no

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F16J15/3472—Means for centering or aligning the contacting faces

Definitions

  • the invention relates to a mechanical seal assembly and more particularly to a gas-lubricated mechanical seal assembly that provides particular advantages when used under high thermal and pressure loads.
  • the cooperating seal rings are sealed and supported by secondary seal members against adjacent components.
  • the secondary sealing elements are usually O-rings or lip seals made of flexible material. Since the sliding rings are not in a pressure-relieved state during operation, at the points where the slip rings are supported by the secondary sealing elements on the adjacent components, as a result of eg thermal expansion relative movements frictional forces occur depending on the height of the prevailing supporting forces more or less can cause large radial forces. These forces can exert on the relevant sliding ring such a tilting moment during operation, which can lead to a change in the sealing gap geometry to an extent that premature wear of the slip rings and / or increased leakage can occur.
  • the invention has for its object to provide an improved mechanical seal assembly of the type mentioned, in which compliance with a desired sealing gap geometry is guaranteed.
  • the harmful influence on the sealing gap geometry of operating forces induced by frictional forces should be minimized.
  • the invention represents an improvement and further development of the arrangement to be taken from EP 1271023 A. Unlike the known arrangement, not only is the rotating seal ring, but also the stationary seal ring is held in loose position, so that both slide rings have a self-aligning property among the ones the forces acting upon it. In addition, both sliding rings are supported on annular planar contact surfaces, create the sealing surfaces, the contact forces are not only accurately determined beforehand, but also minimized. At the support of both sliding rings and their sealing against adjacent components of the mechanical seal assembly no secondary sealing elements made of resilient material involved. Rather, such elements are basically dispensable, since the contact surfaces themselves exercise sealing function, if applied to axial forces according to the inventive design rule.
  • each contact surface should be ⁇ 10 mm, preferably between 0.2 and 2.0, most preferably about 0.6 mm.
  • the abutment surfaces may have a preferred approximately cutting edge-like configuration.
  • each contact surface is designed to be flat by a tolerance amount ⁇ 10 ⁇ m in the circumferential direction and ⁇ 5 ⁇ m in the radial direction. It is preferred that an independent of the respective operating circumstances secondary biasing force with which the rotating Slip rings is spring-biased against its contact surface in addition to a prevailing between the two slip rings main biasing force is between 0.2 N and 10 N per mm circumferential length at the frontal point of the rotating seal ring, at which the secondary spring biasing force acts. This ensures that there is a sufficient sealing effect on this contact surface even at standstill and low hydraulic operating pressures.
  • FIG. 1 is a longitudinal sectional view of a mechanical seal assembly according to the invention after installation in a sealed equipment
  • Fig. 2 is an enlarged view of a first detail of the mechanical seal assembly according to Fig.1, and
  • Fig. 3 is an enlarged view of a second detail of the mechanical seal assembly according to Fig.1.
  • Fig. 1 shows the mechanical seal assembly according to the invention in a sectional view along the upper half with respect to the central longitudinal axis.
  • the reference numeral 1 relates to a seal housing which can be arranged in a housing bore of a tool shank (shown only fragmentarily in the drawing), for example a compressor, and fixed therein in a suitable manner.
  • a shaft 3 is guided through the housing bore.
  • a stationary seal ring 4 is arranged axially movable on a sleeve-shaped support 2, which protrudes axially from the seal housing 1 and either integrally formed thereon or is sealingly mounted as a separate part.
  • a sealing surface 5 is formed at a front side of the stationary seal ring 4, a sealing surface 5 is formed.
  • the sliding ring 4 is secured against rotation relative to the seal housing 1. For this purpose, engage a not shown in the drawing circumferential location of the seal housing 1 axially projecting driving pin (not shown) in a provided on the stationary seal ring 4 aligned recess (also not shown) with a suitably sized game.
  • a suitably sized game As a result, while the stationary seal ring 4 is basically prevented from rotating relative to the seal housing 1, it remains freely movable within the clearance so that it can align in the axial and radial directions.
  • the stationary seal ring 4 is therefore held with Lossitz on the seal housing 1.
  • a main pretensioner e.g. in the form of a main biasing spring 7, which is supported with one end on the seal housing 1, is provided to bias the stationary seal ring 4 with a certain main biasing force.
  • a main biasing spring 7 which is supported with one end on the seal housing 1
  • the invention is not limited to the biasing device shown.
  • the main biasing spring 7 is supported at its other end to an axially movably mounted on the support 2 force transmission ring 8, which at its inner periphery a seal 9 made of resilient material, such as rubber, elastomer or a carbon material, carries, which is in sealing relationship with the outer circumference of the support 2.
  • a seal 9 made of resilient material, such as rubber, elastomer or a carbon material, carries, which is in sealing relationship with the outer circumference of the support 2.
  • something from the power transmission ring 8 axially projecting portion of the secondary seal 9 is also on the sleeve-shaped support 2 axially movably attached support ring 14, which is preferably an annular disc of a material with similar thermal expansion behavior as that of the seal ring 4 can act.
  • a rotating seal ring 11 is placed with Lossitz.
  • the sliding ring 11 has on a front side a sealing surface 12 for cooperation with the sealing surface 5 of the stationary seal ring 4.
  • a driving ring 14 is arranged, which is in frictional engagement with the inner periphery of the sliding ring 11 to provide between the sleeve 10 and the sliding ring 11 such a rotational force transmitting relationship, that on the one hand, the sliding ring 11 is rotated upon rotation of the sleeve 10, while on the other hand, the created by the Lossitz mobility of the seal ring 11 is not or only slightly affected thereby.
  • driver ring 14 may be an O-ring made of a rubber-elastic material, which, however, no or only a negligible low sealing effect needs to come.
  • O-ring instead of an O-ring and an annular coil spring element can be provided with oblique spiraling.
  • Such coil spring elements are known to those skilled in principle and therefore need not be explained in detail.
  • the drive ring 14 also exerts a centering effect on the slide ring 11.
  • the invention is not limited to the above-described type of rotary power transmission from the sleeve 10 to the slide ring 11. Rather, other means accepting this function can also be provided.
  • the rotary seal ring 11 has a rectangular cross-sectional configuration.
  • a flange or support member 17 On the outer circumference of a collar or a shield 18 may be formed, which overlaps the slide ring 11 at least partially outside and against can shield harmful environmental influences.
  • a sufficient clearance is provided, so that the mobility of the slide ring 11 is not limited within suitable game tolerances.
  • annular projection 19 which, as shown in Fig. 2, an annular abutment surface 20 in a radial plane, similar to the annular abutment surface 16 on the projection 15 creates.
  • annular abutment surface 20 At the contact surface 20 of the rotating seal ring 11 is located with its facing away from the sealing surface 12 end face 21 and is thereby axially supported and sealed relative to the support member 17.
  • a sealing gap is formed during operation, which holds the sliding surfaces 5, 12 in a non-contact distance from each other.
  • conveying effective structures are introduced to pump a gaseous medium to be sealed between the sliding surfaces 5, 12 and thereby promote the sealing gap formation.
  • Such effective structures are known in the art and need not be further explained here. It can e.g. on BURGMANN, gas-lubricated mechanical seals, self-published 1988, pages 16 et seq. referenced.
  • Preferred materials for the slip rings 4,11 are hard materials such as tungsten carbide, silicon carbide, silicon nitrite, and tribologically active materials such as carbon material, each in a suitable pairing.
  • a loading ratio (di 2 -d H 2 ) / Cd 1 2 -d 2 2 ) ⁇ 2.0 is preferably between 0.8 and 2, 0, most preferably between 1, 0 and 1, 5 and more preferably about 1, 3 is maintained.
  • di outer diameter of the respective contact surface 16 or 20
  • d 2 inner diameter of the respective contact surface 16 or 20
  • d H diameter of the pressure of the medium to be sealed exposed hydraulic active surface of the Gleitringcruung.
  • the force exerted on the active surface hydraulic pressure causes a force that is superimposed on the prevailing biasing forces under which the slip rings 4, 11 abut the respective contact surfaces 16, 20. In a relative movement between the respective sliding ring and the contact surface, this force can exert a radial component with the aforementioned harmful effect.
  • the dimensions of the two abutment surfaces 16, 20 are further limited to a dimension (di-d 2 ) ⁇ 10 mm, preferably between 0.2 and 2.0, most preferably about 0.6 mm, so that the abutment surfaces have an approximately cutting edge-like character can have.
  • contact surfaces 16, 20 come to lie in an approximately equal radial distance from the central longitudinal axis of the mechanical seal arrangement, which allows a corresponding largely torque-free transmission of the axial forces from one contact surface 16 to the other contact surface 20.
  • a secondary biasing member 24 may be received in an annular groove 22 in the end surface of a sleeve 23 mounted thereon for co-rotation therewith, which may preferably be helical-coil annular coil spring member. which has already been pointed out elsewhere.
  • the secondary biasing member 24 is circumferentially supported on the adjacent end face of the rotating slide ring 11 from and acts on this independent of the main biasing spring 7 certain axial secondary biasing force.
  • the secondary biasing force should be between about 0.2 and 10 N / mm circumferential length of the circumferential location at which the secondary biasing member 24 is supported on the rotary seal ring 11. This provides an improved sealing relationship between the abutment surface 20 and the adjacent face of the rotary seal ring 11 when the mechanical seal assembly is at a standstill.
  • the invention has been described with reference to an embodiment in which the abutment surfaces are provided on projections of the respective support members.
  • the contact surfaces if desired, could also be formed on the slip rings themselves.
  • the conditions on the rotating and stationary sliding ring could be different.
  • the projections may either constitute an integral part of the respective support member or slide ring or thereon suitably subsequently attached inserts.
  • the invention offers particular advantages when used for a gas-lubricated mechanical seal assembly, it could also be used with liquid lubricated assemblies to eliminate or at least increase thermal distortions from a given seal gap geometry minimize.
  • the main biasing means could act instead of on the stationary on the rotating seal ring, which would then have to be arranged axially displaceable on the rotating component.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)
  • Sliding-Contact Bearings (AREA)
  • Sealing Devices (AREA)

Abstract

La présente invention concerne un système de garniture d'étanchéité à bagues coulissantes comprenant une bague coulissante antirotative (4) et une bague coulissante (11) conçue pour effectuer une rotation commune avec une pièce rotative, lesdites bagues étant maintenues respectivement dans un siège mobile et présentant des surfaces d'étanchéité qui coopèrent, sont orientées de façon sensiblement radiale, et sont en prise l'une dans l'autre sous l'effet d'une force de précontrainte principale. Chaque bague de coulissement prend appui axialement au niveau de sa face opposée à la surface d'étanchéité, sur une pièce d'appui (14, 17) par l'intermédiaire d'une surface d'appui (16, 20) annulaire disposée entre la pièce d'appui concernée et la face voisine de la bague de coulissement concernée. Un rapport de charge (d12-dH2) / (d12-d22) est = 2,0, de préférence compris entre 0,8 et 2,0, si possible compris entre 1,0 et 1,5, au mieux égal à environ 1,3, est maintenu au niveau de la surface d'appui (16, 20). Selon l'invention, la dimension (d1-d2) de chaque surface d'appui (16, 20) est = 10 mm, de préférence comprise entre 0,2 et 2,0, au mieux égale à environ 0,6 mm.
PCT/EP2006/006635 2005-07-14 2006-07-06 Systeme de garniture d'etancheite a bagues coulissantes WO2007006493A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EA200800323A EA012134B1 (ru) 2005-07-14 2006-07-06 Система контактных уплотнительных колец
JP2008520762A JP4848008B2 (ja) 2005-07-14 2006-07-06 スライドリングシール構造
US11/922,129 US8523186B2 (en) 2005-07-14 2006-07-06 Slide ring seal arrangement
AT06776137T ATE455265T1 (de) 2005-07-14 2006-07-06 Gleitringdichtungsanordnung
DE502006005919T DE502006005919D1 (de) 2005-07-14 2006-07-06 Gleitringdichtungsanordnung
EP06776137A EP1902239B1 (fr) 2005-07-14 2006-07-06 Systeme de garniture d'etancheite a bagues coulissantes
NO20076214A NO338115B1 (no) 2005-07-14 2007-12-03 Glideringtetningsanordning

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202005011137.6 2005-07-14
DE202005011137U DE202005011137U1 (de) 2005-07-14 2005-07-14 Gleitringdichtungsanordnung

Publications (1)

Publication Number Publication Date
WO2007006493A1 true WO2007006493A1 (fr) 2007-01-18

Family

ID=35070930

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/006635 WO2007006493A1 (fr) 2005-07-14 2006-07-06 Systeme de garniture d'etancheite a bagues coulissantes

Country Status (8)

Country Link
US (1) US8523186B2 (fr)
EP (1) EP1902239B1 (fr)
JP (1) JP4848008B2 (fr)
AT (1) ATE455265T1 (fr)
DE (2) DE202005011137U1 (fr)
EA (1) EA012134B1 (fr)
NO (1) NO338115B1 (fr)
WO (1) WO2007006493A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009087353A1 (fr) 2008-01-11 2009-07-16 John Crane Uk Limited Joints d'étanchéité

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DE202009013496U1 (de) * 2009-10-07 2011-02-17 Eagleburgmann Germany Gmbh & Co. Kg Gleitringdichtungsanordnung mit axial verspanntem Gleitring
DE102010024291B4 (de) 2010-04-23 2013-04-18 Carl Freudenberg Kg Gleitringdichtung mit rotierendem Gegenring mit exakt definierter Einspannung
US8814176B2 (en) * 2011-08-09 2014-08-26 John E. Okonski, Jr. Device for sealing intersecting joints
EP2910823A4 (fr) * 2012-10-19 2016-05-18 Eagleburgmann Japan Co Ltd Joint à soufflets
DE102012022465B4 (de) * 2012-11-15 2014-09-25 Eagleburgmann Germany Gmbh & Co. Kg Gleitringdichtungsanordnung mit verbesserter Nebendichtung
WO2016006535A1 (fr) * 2014-07-11 2016-01-14 イーグル工業株式会社 Joint mécanique
DE102014221000B3 (de) * 2014-10-16 2016-01-21 Eagleburgmann Germany Gmbh & Co. Kg Vormontierter Wechseleinsatz einer Bohrspüleinrichtung
WO2017210715A1 (fr) * 2016-06-10 2017-12-14 Weir Minerals Australia Ltd Joint mécanique
EP3293426A1 (fr) * 2016-09-13 2018-03-14 Siemens Aktiengesellschaft Joint etanche aux gaz
DE102020113068A1 (de) * 2020-05-14 2021-11-18 Eagleburgmann Germany Gmbh & Co. Kg Gleitringdichtungsanordnung für Hochtemperaturanwendungen

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US4212475A (en) 1979-01-15 1980-07-15 Crane Packing Co. Self aligning spiral groove face seal
FR2495727A1 (fr) * 1980-12-08 1982-06-11 Caterpillar Tractor Co Joint a pression de contact constante et equilibree
US5529317A (en) * 1991-06-12 1996-06-25 Flexibox Limited Floating ring seal with return structures and process for making it
EP1271023A2 (fr) 2001-06-29 2003-01-02 Burgmann Dichtungswerke GmbH & Co. KG Garniture mécanique d'étanchéité

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Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4212475A (en) 1979-01-15 1980-07-15 Crane Packing Co. Self aligning spiral groove face seal
FR2495727A1 (fr) * 1980-12-08 1982-06-11 Caterpillar Tractor Co Joint a pression de contact constante et equilibree
US5529317A (en) * 1991-06-12 1996-06-25 Flexibox Limited Floating ring seal with return structures and process for making it
EP1271023A2 (fr) 2001-06-29 2003-01-02 Burgmann Dichtungswerke GmbH & Co. KG Garniture mécanique d'étanchéité

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009087353A1 (fr) 2008-01-11 2009-07-16 John Crane Uk Limited Joints d'étanchéité

Also Published As

Publication number Publication date
JP4848008B2 (ja) 2011-12-28
US8523186B2 (en) 2013-09-03
DE202005011137U1 (de) 2005-09-29
ATE455265T1 (de) 2010-01-15
EA200800323A1 (ru) 2008-06-30
EP1902239A1 (fr) 2008-03-26
EA012134B1 (ru) 2009-08-28
NO338115B1 (no) 2016-08-01
EP1902239B1 (fr) 2010-01-13
JP2009501302A (ja) 2009-01-15
NO20076214L (no) 2008-02-14
DE502006005919D1 (de) 2010-03-04
US20110042903A1 (en) 2011-02-24

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